JP3181244B2 - Vane type fluid motor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a small-sized vane type fluid motor which can be used as a power source of a piping inspection / repair device used in a thermal power plant or a nuclear power plant.

[0002]

2. Description of the Related Art FIG. 6 shows an exploded state of a conventional vane type fluid motor, and FIG. 7 shows a cross section of the conventional vane type fluid motor.

As shown in FIGS. 6 and 7, a conventional vane type fluid motor includes a casing 101 and the casing 101.
A rotary shaft 102 rotatably supported on the rotor 103, a rotor 103 fixed to an outer peripheral portion of the rotary shaft 102, and radially formed in four grooves 104 radially formed on the outer periphery of the rotor 103. A plurality of slidable vanes 105 and a rotor
The casing 101 is provided with a supply port 107 and a discharge port 108 for supplying and discharging a working fluid into and from the casing 101.

That is, the cylindrical casing 101 is divided into three in the axial direction, and comprises a first casing 101a, a second casing 101b and a third casing 101c, which are fastened by three fixing bolts 109. . In the casing 101, each end of the rotating shaft 102 in the axial direction is eccentrically supported via bearings 110a and 110b, and the bearings 110a and 110b are fixed to the fixing screw 111 and the spring washer 1.
Fixed by 12.

As described above, the outer peripheral surface of the rotor 103, the inner peripheral surface and the end surface of the casing 101, and the plurality of vanes 105 form four air chambers 113a to 113d each having a predetermined volume.
Are formed between the rotor 103 and the casing 101, and the plurality of air chambers 113a to 113
The volume of d changes.

Accordingly, the pressurized working fluid is supplied to the supply port.
When supplied to the air chamber 107, it is introduced into the space of the air chamber 113d, and the pressure of the working fluid introduced into the air chamber 113d is increased by two vanes.
Acts on 105, but both vanes near feed port 107
Since the protrusion amounts of the 105 are different, the vane 105 having a large protrusion amount (the upper vane 105 in FIG. 7) receives a larger force than the vane 105 having a small protrusion amount. Therefore, the difference between the received forces becomes a rotational force, the rotor 103 rotates in the direction of the arrow shown in FIG. 7, and the rotating shaft 102 fixed concentrically with the rotor 103 rotates, and the rotating force of the rotating shaft 102 is reduced. The output functions as a motor.

[0007]

As described above, in the conventional vane type fluid motor, when the working fluid is introduced into each of the air chambers 113a to 113d from the supply port 107, the introduced air chambers are introduced. The pressure of 113a to 113d rises and acts on the vane 105, so that the rotor 103 and the rotating shaft 102 can rotate.
That is, the pressure energy of the working fluid is converted into rotational energy. However, most of the energy of the working fluid is pressure energy and kinetic energy, but in this conventional vane type fluid motor, the kinetic energy of the working fluid is not effectively used, and the energy efficiency is not good. There was a problem.

An object of the present invention is to solve such a problem, and an object of the present invention is to provide a vane type fluid motor in which output efficiency is improved.

[0009]

According to a first aspect of the present invention, there is provided a vane type fluid motor which is rotatably supported at an eccentric position of a casing and coaxial with the rotary shaft. A connected rotor, a plurality of vanes slidable along a radial direction in a groove radially provided along an axial direction on an outer periphery of the rotor, and a working fluid supply provided on the casing. A vane-type fluid motor having a port and a discharge port, wherein the inlet port directs fluid to the
When installed so as to flow in the direction of rotation of the rotor,
The kinetic energy of the fluid flowing into the rotor is
And a concave portion for converting into a concave portion is provided .

Further, in the vane type fluid motor according to the present invention, the casing has a cylindrical shape, and
The port is formed along the axial direction of the casing and has an inner periphery.
It is characterized by being provided with an opening on the surface .

Further, in the vane type fluid motor according to the present invention, the plurality of vanes are freely movable in each groove of the rotor.

[0012]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is an exploded view of a vane type fluid motor according to a first embodiment of the present invention, FIG. 2 is an exploded state of a rotor portion of the vane type fluid motor of the present embodiment, and FIG. 3 is a cross section of the vane type fluid motor. Is shown.

The vane type fluid motor of the present embodiment is shown in FIG.
3, a casing 11, a rotating shaft 12 rotatably supported by the casing 11, a rotor 13 fixed to an outer peripheral portion of the rotating shaft 12, and a radial Four grooves 14a, 1 formed in
A plurality of vanes 15a, 15b, 15c, 15d slidable along the radial direction in 4b, 14c, 14d, respectively.
And coil springs 16a, 16b, which push the vanes 15a, 15b, 15c, 15d outward from the rotor 13.
16c and 16d, and the casing 11
The casing 11 is provided with a supply port 17 and a discharge port 18 for supplying and discharging a working fluid into and from the casing 11 .

That is, the cylindrical casing 11 is divided into three parts in the axial direction, and the first casing 11a and the second casing 11a are divided into three parts.
The casing 11b and the third casing 11c,
They are integrally fastened by book fixing bolts 19.
A rotor 13 fixed to a rotating shaft 12 is accommodated in the casing 11, and one end of the rotating shaft 12 is supported at an eccentric position of the first casing 11 a by a bearing 20. It is fixed by a fixing screw 21. The other end of the rotating shaft 12 is second,
The three casings 11b and 11c are supported by bearings 22 and the preload spring washers 23 are interposed therebetween, so that the end face of the rotor 13 and the casing 11
The clearance with the end face can be adjusted. Since the rotating shaft 12 is rotatably supported by the casing 11 in this manner, the rotor 1 fixed to the rotating shaft 12 is
The casing 3 can be freely rotated by the casing 11.

On the other hand, as described above, the outer circumferential surface of the rotor 13 has four grooves 14a, 14b, 1 along the axial direction.
4c and 14d are formed, and these grooves 14a and 14d are formed.
b, 14c and 14d are formed radially from the center of rotation of the rotor 13 at circumferentially equal intervals. The rotor 1 is provided in each of the grooves 14a, 14b, 14c, and 14d.
3, vanes 15a, 15b slidable along the radial direction.
15c and 15d are mounted, and each of the vanes 15
The coils 15a, 15b, 15c and 15d are urged in the direction of pushing them out of the rotor 13 by coil springs 16a, 16b, 16c and 16d mounted in the rotor 13.

Therefore, the rotor 13 is connected to the casing 11
Each vane 15a, 15b, 15
c and 15d are coil springs 16a, 16b, 16c and 16
The outer end of the casing 11 is urged to be pushed outward by d, and the front end portion is in contact with the inner peripheral surface of the casing 11. In this state, the outer peripheral surface of the rotor 13, the inner peripheral surface and the end surface of the casing 11, and the four vanes 15a, 15b, 15c, 15d form four air chambers A, B, C, and C having a predetermined volume. D
Are formed between the rotor 13 and the casing 11 by the same number as the vanes 15a, 15b, 15c, and 15d, and the volume of each of the air chambers A, B, C, and D is changed by the rotation of the rotor 13. .

Further, each vane 15a on the outer peripheral surface of the rotor 13, 15b, 15c, recessed portion 24a is located between the 15d, 24b, 24c, 24d are formed respectively. On the other hand, the above-described supply port 17 includes a supply passage 17a formed in the first casing 11a along the axial direction,
A plurality of supply openings 1 communicating with the supply passage 17a and opening to any of the air chambers A, B, C, and D in the casing 11.
7b and the second and third casings 11b and 11c are connected to the supply path 1
Supply holes 17c, 17d formed so as to communicate with 7a
It is composed of Further, the discharge port 18 is connected to the first port.
A discharge passage 18a formed in the casing 11a along the axial direction and parallel to the supply passage 17a, and is opened to any of the air chambers A, B, C, and D in the casing 11 in communication with the discharge passage 18a. Discharge openings 18b, and discharge holes 18c, 18d formed in the second and third casings 11b, 11c so as to communicate with the discharge passage 18a.

Accordingly, the second and third casings 11b, 1
The working fluid supplied from the supply holes 17c and 17d of 1c is
Through the supply passage 17a of the first casing 11a, the gas flows from each supply opening 17b to any of the air chambers A, B, C, and D, and
By this working fluid, the vanes 15a, 15b, 15c,
The vane-type motor can be made to function by rotating any one of the rotors 13 and the rotating shaft 12 by receiving the rotational force of any one of the motors 15d.

Here, the operation of the above-described vane type fluid motor of this embodiment will be described.

As shown in FIG. 1, the working fluid is second and third working fluids.
The air is supplied to the supply passage 17a of the first casing 11a from the supply holes 17c and 17d of the casings 11b and 11c, and flows into the casing 11 from the supply openings 17b through the supply passage 17a. At this time, the working fluid flows into the air chamber C from the supply opening 17b as shown in FIG.
The rotor 13 and the rotating shaft 12 are rotated by the kinetic energy and pressure energy of the working fluid acting on the rotor. That is, the working fluid flowing into the air chamber C is
c and flows toward the vane 15d side, so that the vane 15d
Receives the rotational force, and the working fluid flows into the air chamber C, so that the pressure increases and the vane 1 having a large pressure receiving area.
The 5d side receives the rotational force, and the rotor 13 rotates together with the rotating shaft 12 by the rotational force obtained by converting the two types of energy.

When the rotor 13 is rotated by the working fluid flowing into the air chamber C, the working fluid flows into the air chamber B, and the vane 15c receives a rotational force. The working fluid flows in the order of D, and the rotor 13 and the rotating shaft 12 rotate continuously. On the other hand, each air chamber A,
When B, C, and D rotate by a predetermined angle to communicate with the discharge opening 18b and the volume sharply decreases, each of the air chambers A, B, C, and
The working fluid in D is discharged from the discharge opening 18b to the discharge path 18a.
Through the second and third casings 11b, 11c
8c and 18d.

As described above, in the vane type fluid motor according to the present embodiment, the vanes 15a, 15b, 15c and 15d and the formation of the recesses 24a, 24b, 24c and 24d allow the working fluid flowing into the air chambers A, B, C and D from the supply port 17 to collide with the recesses 24c and cause vanes. 1
Acting on 5a, 15b, 15c, 15d, the rotor 13 and the vanes 15a, 15b, 15c, 15d rotate with the rotating shaft 12 by kinetic energy and pressure energy. Therefore, the output energy of the motor is improved by efficiently converting the energy of the fluid into rotational force. On the other hand, when the rotor 13 rotates, the working fluid in each of the air chambers A, B, C, and D rapidly decreases in volume and is discharged from the discharge port 18 while maintaining a high pressure.
a, 24b, 24c, and 24d, the minimum volume is increased. Therefore, in this discharge step, the compression rate of the working fluid is reduced and the back pressure is reduced, so that the output loss is suppressed and the output efficiency of the motor is reduced. improves.

As a result, for example, a diameter of 30 mm and a length of 1
It is as small as 00mm and output 500W (supply pressure 6kgf / c
m ² ), and an air motor with a large output can be realized.
Applicable to machining in a pipe of about 0 mm.

FIG. 4 shows a cross section of a vane type fluid motor according to a second embodiment of the present invention. Note that members having the same functions as those described in the above-described embodiment are denoted by the same reference numerals, and redundant description will be omitted.

The vane type fluid motor according to the present embodiment is shown in FIG.
As shown in FIG. 1, a rotary shaft 12 is rotatably supported in a casing 11, a rotor 31 is fixed to the rotary shaft 12, and four grooves 3 formed on the outer periphery of the rotor 31 are provided.
The vanes 33a, 3 are provided in 2a, 32b, 32c, 32d.
3b, 33c, 33d are slidably mounted along the radial direction, respectively, and the vanes 33a, 33b, 3
3c and 33d are urged outward by a coil spring (not shown). Further, each vane 33a on the outer peripheral surface of the rotor 31, 33b, 33c, the blade 35a by forming a recessed portion 34 is located between the 33d, 35b,
35c and 35d are formed respectively.

The casing 11 is provided with a supply port 17 and a discharge port 18 for supplying and discharging a working fluid to each of the air chambers A, B, C, and D of the casing 11.

Accordingly, when the working fluid is supplied from the supply port 17 into the casing 11, the working fluid first flows into the air chamber C, and the kinetic energy and the pressure energy cause the rotor 31 and the rotating shaft 12 to rotate. I do. That is, the working fluid flowing into the air chamber C is
From the vane 33d and the blade 35c,
Since the vane 33d flows to the 3d side, in addition to the vane 33d receiving the rotational force, the working fluid flows into the air chamber C, the pressure increases, and the vane 33d having a large pressure receiving area receives the rotational force. The two types of energy rotate together with the rotating shaft 12 by the converted torque.
When the rotor 31 rotates, the working fluid flows into the air chambers B,
A and D flow in order, and the rotor 13 and the rotating shaft 12 rotate continuously. On the other hand, when each of the air chambers A, B, C, and D rotates by a predetermined angle and communicates with the discharge port 18 and the volume rapidly decreases, the working fluid in each of the air chambers A, B, C, and D is discharged from the discharge port. Discharged from 18.

As described above, in the vane type fluid motor of the present embodiment, the rotor 31 is provided with the vanes 33a, 33b, 33c, 33d which are movable in the radial direction, and the plurality of recesses 34 form the blades 35a, 35b, 35
With the formation of c, 35d, the working fluid flowing into each of the air chambers A, B, C, D from the supply port 17 acts on the recess 34 and the blades 35a, 35b, 35c, 35d, and the rotor 31 and the vanes 33a, 33b, 33c and 33d rotate with the rotating shaft 12 by kinetic energy and pressure energy. Therefore, the output energy of the motor is improved by efficiently converting the energy of the fluid into rotational force. On the other hand, when the rotor 31 rotates, the air chambers A, B, C,
The working fluid in D is discharged from the discharge port 18 while the volume is rapidly reduced and remains at a high pressure. However, since the minimum volume is large, the compression rate of the working fluid is reduced in this discharging step to reduce the back pressure. , The output loss is suppressed, and the output efficiency of the motor is improved.

FIG. 5 shows an exploded state of a rotor portion of a vane type fluid motor according to a third embodiment of the present invention. Note that members having the same functions as those described in the above-described embodiment are denoted by the same reference numerals, and redundant description will be omitted.

The vane type fluid motor according to the present embodiment is shown in FIG.
As shown in FIG. 1, a rotating shaft 12 is rotatably supported in a casing 11, and a rotor 41 is fixed to the rotating shaft 12, and four grooves 4 formed on the outer periphery of the rotor 41.
The vanes 43a, 4 are provided in 2a, 42b, 42c, 42d.
3b, 43c and 43d are slidably mounted along the radial direction, respectively, and the vanes 43a, 43c
b, 43c, the concave portion 44 between 43d are formed respectively. In the rotor 41 of the present embodiment, the vanes 43a, 43b, 43c, 4
3d is not biased and supported by the coil spring.

Therefore, when the working fluid is supplied into the casing from a supply port (not shown), the kinetic energy and the pressure energy of the working fluid are converted into rotational force, and the rotor 41 and the rotating shaft 12 rotate. At this time, since each vane 43a, 43b, 43c, 43d is not biased and supported by the coil spring, each vane 43a, 43
The tips of b, 43c and 43d are not always in contact with the inner peripheral surface of the casing, and the respective air chambers are not completely closed spaces. However, the working fluid flowing into the air chamber collides with the concave portion 44 of the rotor 41, and the vanes 43a, 43b, 43
c, 43d, so that the vanes 43a, 43
b, 43c, and 43d receive the rotational force and start rotating at a low speed. Then, the centrifugal force acts on the vanes 43a, 43b, 43c, 43d by the rotation of the rotor 41, and the front end contacts the inner peripheral surface of the casing, so that the air chamber becomes a closed space. Therefore, when the working fluid flows into the air chamber, the pressure rises, and the vanes 43a, 43b, 43c, 43d receive a rotational force, and the rotor 41 moves together with the rotating shaft 12 by the rotational force obtained by converting the kinetic energy and the pressure energy. Rotate.

As described above, in the vane type fluid motor of the present embodiment, in addition to the operation and effect of the above-described first embodiment, the vanes 43a, 43b, 43c and 43d are brought into contact with the inner peripheral surface of the casing. No coil spring is required,
The number of parts is reduced and the number of assembling steps is reduced, and the tips of the vanes 43a, 43b, 43c and 43d are not always in contact with the inner peripheral surface of the casing, so that the rotational loss of the rotor 41 due to frictional resistance can be reduced. With vanes 43a, 4
3b, 43c, and 43d can be reduced in amount of wear, and manufacturing cost can be reduced, efficiency can be increased, and life can be extended.

In the vane type fluid motor of the present invention, the shapes and dimensions of the rotor and the vane are not limited to those described in the above embodiments, but may be changed as appropriate according to the conditions of use. .

[0035]

As described in detail in the above embodiment, according to the vane type fluid motor of the first aspect,
A rotor is connected to a rotating shaft rotatably supported at an eccentric position of a casing , and a plurality of vanes slidable along a radial direction in grooves radially provided along an axial direction on an outer periphery of the rotor. The casing is provided with a supply port and a discharge port for the working fluid .
The rotor is provided so that it flows in the direction of rotation of the rotor.
To convert the kinetic energy of the flowing fluid into rotational force.
Since the concave portion is provided, the kinetic energy and the pressure energy of the fluid can be efficiently converted into rotational force to rotate the rotating shaft, and the output efficiency of the motor can be improved.

Further, according to the vane type fluid motor of the second aspect of the invention, the casing is formed in a cylindrical shape, and the supply port is connected to the casing.
Formed along the axial direction of the
Since girder, by rotating feed the fluid from the inlet port can be guided in the direction of rotation of efficient the rotor, the rotating shaft by converting the kinetic energy and pressure energy of the fluid efficiently rotational force, a motor Output efficiency can be improved.

According to the vane type fluid motor of the third aspect of the present invention, since the plurality of vanes are freely movable in each groove of the rotor, the kinetic energy of the fluid is converted into rotational force. Since the rotating shaft is rotated, there is no need for an urging member for pressing the vane against the inner surface of the casing, so that the number of parts can be reduced and the number of assembling steps can be reduced. The rotation loss of the rotor can be reduced, and the amount of wear of the vane can be reduced. As a result, the manufacturing cost can be reduced,
Higher efficiency and longer life can be achieved.

[Brief description of the drawings]

FIG. 1 is an exploded view of a vane type fluid motor according to a first embodiment of the present invention.

FIG. 2 is an exploded view of a rotor portion of the vane type fluid motor according to the embodiment.

FIG. 3 is a sectional view of a vane type fluid motor.

FIG. 4 is a sectional view of a vane type fluid motor according to a second embodiment of the present invention.

FIG. 5 is an exploded view of a rotor portion of a vane type fluid motor according to a third embodiment of the present invention.

FIG. 6 is an exploded view of a conventional vane type fluid motor.

FIG. 7 is a sectional view of a conventional vane type fluid motor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 11 Casing 12 Rotating shaft 13 Rotor 14a, 14b, 14c, 14d Groove 15a, 15b, 15c, 15d Vane 16a, 16b, 16c, 16d Coil spring 17 Supply port 17a Air supply path 17b Air supply opening 18 Discharge port 18a Discharge path 18b discharge opening 24a, 24b, 24c, 24d recess 31 rotor 32a, 32b, 32c, 32d grooves 33a, 33b, 33c, 33d vane 34 recess 35a, 35b, 35c, 35d blade root 41 rotor 42a, 42b, 42c, 42d grooves 43a, 43b, 43c, 43d vane 44 recess A, B, C, D air chamber

 ──────────────────────────────────────────────────続 き Continuation of front page (56) References JP-A-58-2488 (JP, A) JP-A-57-75 (JP, U) JP-A-56-31666 (JP, U) Registered utility model 3001012 ( JP, U)

Claims (3)

(57) [Claims] 1. A rotating shaft rotatably supported at an eccentric position of a casing , a rotor coaxially connected to the rotating shaft, and a groove radially provided on an outer periphery of the rotor along an axial direction. and slidable plurality of vanes in the radial direction, the vane type fluid motor equipped with a sheet inlet port and the discharge port for a working fluid provided in the casing, before
The inlet port allows fluid to flow in the direction of rotation of the rotor.
And the fluid flowing into the rotor
A vane-type fluid motor characterized by having a concave portion for converting the kinetic energy into rotational force . 2. The vane-type fluid motor according to claim 1, wherein the casing has a cylindrical shape, and the supply port is provided.
Is formed along the axial direction of the casing and opens on the inner peripheral surface.
A vane-type fluid motor provided by mouth . 3. The vane type fluid motor according to claim 1, wherein said plurality of vanes are freely movable in respective grooves of said rotor.